WO2006068262A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
WO2006068262A1
WO2006068262A1 PCT/JP2005/023695 JP2005023695W WO2006068262A1 WO 2006068262 A1 WO2006068262 A1 WO 2006068262A1 JP 2005023695 W JP2005023695 W JP 2005023695W WO 2006068262 A1 WO2006068262 A1 WO 2006068262A1
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WO
WIPO (PCT)
Prior art keywords
wall
flat tubes
heat exchanger
flat
forming
Prior art date
Application number
PCT/JP2005/023695
Other languages
English (en)
Inventor
Koichiro Take
Shigeharu Ichiyanagi
Original Assignee
Showa Denko K.K.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Showa Denko K.K. filed Critical Showa Denko K.K.
Priority to DE112005003260T priority Critical patent/DE112005003260T5/de
Publication of WO2006068262A1 publication Critical patent/WO2006068262A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0391—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits a single plate being bent to form one or more conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers

Definitions

  • the present invention relates to a heat exchanger , and more particularly to a heat exchanger' suitable for use as a gas cooler of a supercritical refrigeration cycle which employs a supercritical refrigerant such as CO 2 and in which the pressure of the refrigerant on a high-pressure side is equal to or higher than the critical pressure of the refrigerant .
  • the term “aluminum” encompasses aluminum alloys in addition to pure aluminum .
  • the term “supercritical refrigeration cycle” refers to a refrigeration cycle in which the pressure of refrigerant exceeds the critical pressure and enters a supercritical state on a high- pressure side
  • the term “supercritical refrigerant” refers to a refrigerant used in the supercritical refrigeration cycle .
  • a conventionally known heat exchanger of a supercritical refrigeration cycle in which a supercritical refrigerant such as CO 2 is used includes , for example , a pair of headers arranged in parallel with and apart from each other; a plurality of flat tubes of aluminum arranged in parallel between the two headers and each having opposite end portions connected to the respective headers ; corrugate fins of aluminum arranged in corresponding air-passing clearances between adjacent flat tubes ; a refrigerant inlet connected to an upper end portion of a circumferential wall of a first header; a refrigerant outlet connected to a lower end portion of a circumferential wall of a second header; a first partition wall provided in the interior of the first header at a vertically intermediate position ; and a second partition wall provided in the interior of the second header at a position located below a vertically intermediate position of the second header .
  • All the flat tubes are divided into a tube group consisting of a plurality of flat tubes located above the first partition wall , a tube group consisting of a plurality of flat tubes located between the first and second partition walls , and a tube group consisting of a plurality of flat tubes located below the second partition wall , thereby being divided into first to third passes ( refrigerant channel groups ) .
  • first to third passes refrigerant channel groups
  • the refrigerant flows in the same direction through the flat tubes which constitute the pass .
  • Two adjacent passes differ in the flow direction of the refrigerant flowing through the flat tubes thereof .
  • the number of flat tubes is reduced in sequence from the first pass to the third pass .
  • the refrigerant flows in the heat exchanger in a meandering manner on the basis of the passes ( refer to , for example , Japanese Patent No . 3313086 ) .
  • the heat exchanger described in the patent provides a certain degree of heat radiation performance .
  • various studies conducted by the inventors of the present invention have revealed that a further improvement in heat radiation performance and a reduction in size and weight by virtue of the improved heat radiation performance cannot be expected from the heat exchanger described in the patent , for the reason described below.
  • An object of the present invention is to overcome the above problems and to provide a heat exchanger which , when used as a gas cooler of a supercritical refrigeration cycle , exhibits improved heat radiation performance and allows a reduction in size and weight .
  • the present invention comprises the following modes .
  • a heat exchanger including a pair of headers arranged apart from each other , and a plurality of flat tubes arranged between the two headers at predetermined intervals along the longitudinal direction of the headers and each having opposite end portions connected to the respective headers , wherein all the flat tubes are divided into two passes each consisting of a plurality of flat tubes continuously arranged in the vertical direction ; and when the quotient produced by dividing the number of the flat tubes constituting each of the passes by the number of all the flat tubes is defined as " tube ratio , " each of the passes has a tube ratio of 0.45 to 0.55.
  • a heat exchanger including a pair of headers arranged apart from each other , and a plurality of flat tubes arranged between the two headers at predetermined intervals along the longitudinal direction of the headers and each having opposite end portions connected to the respective headers , wherein all the flat tubes are divided into three passes each consisting of a plurality of flat tubes continuously arranged in the vertical direction ; and when the quotient produced by dividing the number of the flat tubes constituting each of the passes by the number of all the flat tubes is defined as " tube ratio , " each of the passes has a tube ratio of 0.3 to 0.4.
  • each of the flat tubes has a plurality of refrigerant channels arranged therein along the width direction thereof ; each of the refrigerant channels has a vertically elongated cross section ; and when the quotient produced by dividing a channel height Hp ( mm) of the refrigerant channel by a minimum channel width Wp (mm ) of the refrigerant channel is defined as " aspect ratio , " the aspect ratio ( Hp/Wp ) is 1.05 to 2.
  • the minimum channel width Wp of the refrigerant channel means the width of the refrigerant channel .
  • the minimum channel width Wp means the width of the refrigerant channel as measured at a certain height where the refrigerant channel is the narrowest .
  • a heat exchanger according to par . 1 ) or 3 ) , satisfying a relation Sp/Sb ⁇ 0.5 , where Sp (mm 2 ) is the total channel cross-sectional-area of all the refrigerant channels of each of the flat tubes , and Sb (mm 2 ) is the remaining area ( cross-sectional area of a bulk portion ) after subtracting the total channel cross-sectional-area Sp (mm 2 ) from the entire cross -sectional area of each of the flat tubes .
  • each of the flat tubes includes two flat walls in parallel with each other; first and second side walls extending over corresponding side ends of the two flat walls ; and reinforcement walls provided between the first and second side walls and extending between the two flat walls and in the longitudinal direction of the two flat walls ; and each of the flat tubes is formed from a single metal sheet including two flat-wall-forming portions ; a connection portion connecting the two flat-wall-forming portions and adapted to form the first side wall ; two side-wall-forming elongated projections provided integrally with and in such a manner as to project from corresponding side ends of the flat-wall-forming portions opposite the connection portion , and adapted to form the second side wall ; a plurality of reinforcement-wall-forming elongated projections provided integrally with each of the flat-wall-forming portion in such a manner as to project in the same direction as the side- wall-forming elongated projections ; and the flat tube is formed by folding
  • a heat exchanger according to par . 12 ) wherein of two reinforcement-wall-forming elongated projections which form each reinforcement wall , one reinforcement-wall-forming elongated projection has a groove which is formed on the tip end face thereof so as to receive a tip end portion of the other reinforcement-wall-forming elongated projection .
  • corrugate fins each including wave crest portions , wave trough portions , and connection portions each connecting together a wave crest portion and a wave trough portion are each arranged between the adjacent flat tubes ; and each corrugate fin has a fin height of 5 mm to 8 mm, a fin pitch of 1.0 mm to 1.5 mm, and a thickness of 0.05 mm to 0.1 mm.
  • a supercritical refrigeration cycle which comprises a compressor , a gas cooler , an evaporator , a pressure- reducing device , and an intermediate heat exchanger for performing heat exchange between refrigerant flowing out from the gas cooler and refrigerant flowing out from the evaporator and in which a supercritical refrigerant is used, wherein the gas cooler is a heat exchanger according to par. 1 ) or 3 ) .
  • all the flat tubes are divided into two passes each consisting of a plurality of flat tubes continuously arranged in the vertical direction .
  • the refrigerant velocity in the refrigerant channels of the flat tubes is increased, there can be prevented an increase in pressure loss generated in the refrigerant channels , as well as a drop in refrigerant flow rate which could otherwise result from an increase in pressure loss .
  • the quotient produced by dividing the number of the flat tubes constituting each of the passes by the number of all the flat tubes is defined as "tube ratio, " each of the passes has a tube ratio of 0.45 to 0.55 , preferably 0.48 to 0.52.
  • the heat exchanger when used as a gas cooler of a supercritical refrigeration cycle , there can be prevented an increase in pressure loss generated in the refrigerant channels of the flat tubes of either pass , as well as a drop in refrigerant flow rate in either pass which could otherwise result from an increase in pressure loss . Accordingly , when the heat exchanger is used as a gas cooler of a supercritical refrigeration cycle , the heat exchanger exhibits improved heat radiation performance as compared with the heat exchanger described in the above-mentioned patent and thus allows a reduction in size and weight .
  • all the flat tubes are divided into three passes each consisting of a plurality of flat tubes continuously arranged in the vertical direction .
  • the refrigerant velocity in the refrigerant channels of the flat tubes is increased, there can be prevented an increase in pressure loss generated in the refrigerant channels , as well as a drop in refrigerant flow rate which could otherwise result from an increase in pressure loss .
  • the quotient produced by dividing the number of the flat tubes constituting each of the passes by the number of all the flat tubes is defined as "tube ratio , " each of the passes has a tube ratio of 0.3 to 0.4 , preferably 0.32 to 0.34.
  • the heat exchanger when used as a gas cooler of a supercritical refrigeration cycle , there can be prevented an increase in pressure loss generated in the refrigerant channels of the flat tubes of any one of the passes , as well as a drop in refrigerant flow rate in any one of the passes which could otherwise result from an increase in pressure loss . Accordingly, when the heat exchanger is used as a gas cooler of a supercritical refrigeration cycle , the heat exchanger exhibits improved heat radiation performance as compared with the heat exchanger described in the above-mentioned patent and thus allows a reduction in size and weight .
  • the heat exchanger described in any one of pars . 5 ) to 11 ) exhibits improved heat radiation performance , and enhanced withstand pressure of the flat tubes .
  • the heat exchanger described in par . 14 exhibits improved heat radiation performance while suppressing an increase in pressure loss of air flowing through clearances between adjacent flat tubes , thereby maintaining good balance therebetween .
  • FIG . 1 is a general front view showing Embodiment 1 of a heat exchanger according to the present invention .
  • FIG . 2 is a cross-sectional views showing a flat tube of the heat exchanger of FIG . 1.
  • FIG . 3 is a fragmentary enlarged view of FIG . 2.
  • FIG . 4 is a general front view showing Embodiment 2 of a heat exchanger according to the present invention .
  • FIG . 5 is a graph showing the results of Experiment Examples 1 and 2 and Comparative Experiment Examples 3 and 4.
  • FIG . 6 is a graph showing the results of Experiment Example 1 and Comparative Experiment Example 1.
  • FIG . 7 is a graph showing the results of Experiment Example 2 and Comparative Experiment Example 2.
  • FIG. 1 is a general front view showing Embodiment 1 of a heat exchanger according to the present invention .
  • FIG . 2 is a cross-sectional views showing a flat tube of the heat exchanger of FIG . 1.
  • FIG. 8 is a cross-sectional view showing a first modified embodiment of the flat tube .
  • FIG . 9 is a fragmentary enlarged view of FIG . 8.
  • FIG . 10 is a set of views showing a method of manufacturing the flat tube shown in FIG . 8.
  • FIG . 11 is a cross-sectional view showing a second modified embodiment of the flat tube .
  • FIG . 12 is a cross-sectional view showing a third modified embodiment of the flat tube .
  • FIG. 13 is a fragmentary enlarged view of FIG . 12.
  • FIG . 14 is a set of views showing a method of manufacturing the flat tube shown in FIG . 12.
  • FIG . 15 is a cross-sectional view showing a fourth modified embodiment of the flat tube .
  • FIG . 16 is a fragmentary enlarged view of FIG . 15.
  • FIG . 17 is a set of views showing a method of manufacturing the flat tube shown in FIG . 15.
  • FIG . 1 shows the overall structure of a heat exchanger according to the present invention
  • FIGS . 2 and 3 show the structures of essential portions thereof .
  • a heat exchanger 1 includes a pair of left- hand and right-hand headers 2 , 3 of aluminum arranged apart from and in parallel with each other and extending vertically; a plurality of flat tubes 4 of aluminum arranged in parallel between the two headers 2 , 3 , separated from one another in the vertical direction , and each having opposite end portions connected to the respective headers 2 , 3 ; corrugated fins 6 of aluminum arranged in respective air passage clearances 5 between adjacent flat tubes 4 and outside the uppermost and lowermost flat tubes 4 , and brazed to the flat tubes 4 ; side plates 7 of aluminum arranged externally of and brazed to the respective uppermost and lowermost corrugate fins 6 ; a refrigerant inlet 8 provided on a side wall of the right-hand header 3 and located above a vertically intermediate position ; a refrigerant outlet 9 provided on the side wall of the right-hand header 3 and located below the vertically intermediate position; and a partition wall 10 provided in the interior of the right-hand
  • All the flat tubes 4 are divided into a tube group consisting of a plurality of the flat tubes 4 located above the partition wall 10 , and a tube group consisting of a plurality of the flat tubes 4 located below the partition wall 10 , thereby being divided into first and second passes Pl , P2 ( refrigerant channel groups ) .
  • first and second passes Pl , P2 refrigerant channel groups .
  • the refrigerant flows in the same direction through the flat tubes 4 which constitute the pass Pl , P2.
  • the two passes Pl , P2 differ in the flow direction of the refrigerant flowing through the flat tubes 4 thereof .
  • each of the passes Pl , P2 has a tube ratio of 0.45 to 0.55.
  • the total of the tube ratio of the first pass Pl and the tube ratio of the second pass P2 is 1.
  • the heat exchanger 1 In the case where the heat exchanger 1 is used as a gas cooler of a supercritical refrigeration cycle which employs a supercritical refrigerant such as CO 2 , a tube ratio less than 0.45 or in excess of 0.55 causes an increase in pressure loss generated in the flat tubes 4 in either pass Pl , P2 and a drop in refrigerant flow rate in either pass Pl , P2 , resulting in an impairment in heat radiation performance .
  • the size of the heat exchanger 1 must be increased , which is accompanied by an increase in weight .
  • the passes Pl , P2 each have a tube ratio of 0.48 to 0.52. Even in this case, the total of the tube ratio of the first pass Pl and the tube ratio of the second pass P2 is 1.
  • each of the flat tubes 4 is formed from an extrudate ; all the flat tubes 4 have the same cross-sectional shape ; and a plurality of refrigerant channels 11 are formed in the flat tubes 4 and are arranged in a row in the width direction of flat tubes 4.
  • Each of the refrigerant channels 11 has an identical cross-sectional shape of a rectangle standing on its shorter side , except for those at the opposite ends .
  • Hp (mm) represents the channel height of each of the refrigerant channels 11 ; Wp (mm) represents the minimum channel width of each of the refrigerant channels 11 ; Tw (mm) represents the thickness of a partition wall 12 between the adjacent refrigerant channels 11 of each of the flat tubes 4 ; Ht (mm) represents the tube height of each of the flat tubes 4 , Sp (mm 2 ) represents the total channel cross- sectional-area of all the refrigerant channels 11 of each of the flat tubes 4 ( the total area of hatched portions in FIG . 2 ( b ) ) ; Sb (mm 2 ) represents the remaining area ( the area of a hatched bulk portion in FIG .
  • the width of each of the refrigerant channels 11 of each flat tube 4 remains unchanged along the entire height of the refrigerant channel 11 , except for the refrigerant channels 11 at the opposite ends .
  • the width of each of the refrigerant channels 11 is the minimum channel width Wp .
  • the width of each of the refrigerant channels 11 at the opposite ends changes in the height direction , and needless to say, the minimum channel width Wp is the width of the narrowest potion .
  • the corrugate fins 6 each include wave crest portions , wave trough portions , and connection portions each connecting together a wave crest portion and a wave trough portion .
  • the fin height Hf of each corrugate fin 6 is the direct distance between the wave crest portion and the wave trough portion , and the fin height Hf is preferably 5 mm to 8 mm.
  • the fin pitch Pf of each corrugate fin 6 is the distance between the central portions (with respect to the left-right direction ) of a wave crest portion and a wave trough portion adjacent thereto ; i . e .
  • each corrugate fin 6 is 0.05 mm to 0.1 mm.
  • This embodiment is shown in FIG . 4.
  • FIG. 4 shows the overall structure of a heat exchanger according to the present invention .
  • the refrigerant inlet 8 is provided at an upper end portion of a side wall of the left-hand header 2
  • the refrigerant outlet 9 is provided at a lower end portion of a side wall of the right-hand header 3.
  • a first partition wall 21 is provided in the interior of the left-hand header 2 and is located above a vertically intermediate position .
  • a second partition wall 22 is provided in the interior of the right-hand header 3 and is located below a vertically intermediate position .
  • All the flat tubes 4 are divided into a tube group consisting of a plurality of the flat tubes 4 located above the first partition wall 21 , a tube group consisting of a plurality of the flat tubes 4 located between the two partition walls 21 , 22 , and a tube group consisting of a plurality of the flat tubes 4 located below the second partition wall 22 , thereby being divided into first to third passes Pl , P2 , P3 ( refrigerant channel groups ) .
  • first to third passes Pl , P2 , P3 refrigerant channel groups
  • each of the passes Pl , P2 , P3 has a tube ratio of 0.3 to 0.4.
  • the heat exchanger 20 is used as a gas cooler of a supercritical refrigeration cycle which employs a supercritical refrigerant such as CO 2
  • a tube ratio less than 0.3 or in excess of 0.4 causes an increase in pressure loss generated in the flat tubes 4 in any one of the passes Pl , P2 , P3 and a drop in refrigerant flow rate in any one of the passes Pl , P2 , P3 , resulting in an impairment in heat radiation performance .
  • the size of the heat exchanger 20 must be increased, which is accompanied by an increase in weight .
  • the passes Pl , P2 , P3 each have a tube ratio of 0.32 to 0.34.
  • Each of the heat exchangers 1 , 20 of Embodiments 1 and 2 is suitable for use as a gas cooler in a supercritical refrigeration cycle which includes a compressor , a gas cooler , an evaporator , an accumulator serving as a gas- liquid separator , an expansion valve serving as a pressure- reducing device , and an intermediate heat exchanger for performing heat exchange between a high-temperature , high- pressure refrigerant flowing out from the gas cooler and a low-temperature , low-pressure refrigerant flowing out from the evaporator and passing through the accumulator and which employs CO 2 as a supercritical refrigerant .
  • the supercritical refrigeration cycle is mounted on a vehicle such as an automobile as a car air conditioner .
  • CO 2 is used as a supercritical refrigerant of a supercritical refrigeration cycle
  • the refrigerant is not limited thereto , but ethylene , ethane , nitrogen oxide , or the like may also be used .
  • the present Experiment Example is of an experiment which was conducted by use of the heat exchanger 1 of Embodiment 1.
  • Specifications of heat exchanger height Hc of heat exchange core section composed of flat tubes 4 and corrugate fins 6 : 380 mm; width Wc of heat exchange core section : 660 mm; total number of flat tubes 4 : 51 ; number of flat tubes 4 of first pass Pl : 26 ( tube ratio 0.51 ) ; and number of flat tubes 4 of second pass P2 : 25 ( tube ratio 0.49 ) .
  • flat tube 4 channel height Hp of refrigerant channel 11 : 0.44 mm; minimum channel width Wp of refrigerant channel 11 : 0.32 mm; thickness Tw of partition wall 12 between adjacent refrigerant channels 11 : 0.38 mm; tube height Ht : 1.3 mm; total channel cross-sectional-area of all refrigerant channels 11 : 3.1 mm 2 ; remaining area Sb after subtracting total channel cross-sectional-area Sp (mm 2 ) from entire cross-sectional area of flat tube 4 : 17.3 mm 2 ; and tube width Wt : 16 mm.
  • the present Experiment Example is of an experiment which was conducted by use of the heat exchanger 20 of Embodiment 2.
  • Dimensions of the heat exchange core section, the total number of flat tubes 4 , dimensions (Ht , Sp) of the flat tube 4 , the aspect ratio , Tw/Wp , Hp/Ht , Sp/Sb , and (Wt x Ht ) /3 are identical with those of Experiment Example 1.
  • Three passes Pl , P2 , P3 each have 17 flat tubes 4 and a tube ratio of 0.33.
  • the present comparative experiment was conducted by use of a 3-pass heat exchanger which was similar to that of Experiment Example 2 except for the following : number of flat tubes 4 of first pass : 29 ( tube ratio 0.57 ) ; number of flat tubes 4 of second pass : 14 ( tube ratio 0.27 ) ; and number of flat tubes 4 of third pass : 8 ( tube ratio 0.16 ) .
  • the heat exchanger was measured for heat radiation performance and pressure loss generated in the refrigerant channels 11 of the flat tubes 4 in a manner similar to that of Experiment Example 1. Comparative Experiment Example 3
  • the present comparative experiment was conducted by use of a heat exchanger which was similar to that of Experiment Example 1 except that all the flat tubes 4 were divided into four passes and except for the following : number of flat tubes 4 of first pass : 13 ( tube ratio 0.25 ) ; number of flat tubes 4 of second pass : 13 ( tube ratio 0.25 ) ; number of flat tubes 4 of third pass : 13 ( tube ratio 0.25 ) ; and number of flat tubes 4 of fourth pass : 12 ( tube ratio 0.24 ) .
  • the heat exchanger was measured for heat radiation performance and pressure loss generated in the refrigerant channels 11 of the flat tubes 4 in a manner similar to that of Experiment Example 1.
  • FIG . 5 shows the results of Experiment Examples 1 and 2 and Comparative Experiment Examples 3 and 4.
  • the bar graph shows heat radiation performance
  • the line graph shows pressure loss . Heat radiation performance and pressure loss are represented with those of Experiment Example 1 taken as 100% .
  • FIG. 6 shows the results of Experiment Example 1 and Comparative Experiment Example 1.
  • the bar graph shows heat radiation performance
  • the line graph shows pressure loss . Heat radiation performance and pressure loss are represented with those of Experiment Example 1 taken as 100% .
  • FIG . 7 shows the results of Experiment Example 2 and Comparative Experiment Example 2.
  • the bar graph shows heat radiation performance
  • the line graph shows pressure loss . Heat radiation performance and pressure loss are represented with those of Experiment Example 2 taken as 100% .
  • a flat tube 30 shown in FIGS . 8 and 9 includes mutually opposed flat upper and lower walls 31 , 32 ( a pair of flat walls ) ; left and right side walls 33 , 34 which extend, over left and right side ends , respectively, of the upper and lower walls 31 , 32 ; and a plurality of reinforcement walls 35 which are provided at predetermined intervals between the left and right side walls 33 , 34 and extend longitudinally and between the upper and lower walls 31 , 32.
  • the flat tube 30 internally has a plurality of refrigerant channels 36 arranged in the width direction thereof .
  • the reinforcement walls 35 serve as partition walls between adjacent refrigerant channels 36.
  • the width of each refrigerant channel 36 remains unchanged along the entire height of the refrigerant channel 36. Further , the width of the refrigerant channel 36 at the right end is smaller than those of the remaining refrigerant channels 36 , and the remaining refrigerant channels 36 have the same width .
  • the left side wall 33 has a dual structure and includes an outer side-wall-forming elongated projection 37 which is integrally formed with the left side end of the upper wall 31 in a downward raised condition and extends along the entire height of the flat tube 30 ; an inner side-wall-forming elongated projection 38 which is located inside the outer side-wall-forming elongated projection 37 and is integrally formed with the upper wall 31 in a downward raised condition ; and an inner side-wall-forming elongated projection 39 which is integrally formed with the left side end of the lower wall 32 in an upward raised condition .
  • the outer side-wall- forming elongated projection 37 is brazed to the two inner side-wall-forming elongated projections 38 , 39 and to the lower wall 32 while a lower end portion thereof is engaged with a left side edge portion of the lower surface of the lower wall 32.
  • the two inner side-wall-forming elongated projections 38 , 39 are brazed together while butting against each other .
  • a right side wall 34 is integrally formed with the upper and lower walls 31 , 32.
  • a projection 39a is integrally formed on the tip end face of the inner side-wall- forming projection 39 of the lower wall 32 and extends in the longitudinal direction of the inner side-wall-forming projection 39 along the entire length thereof .
  • a groove 38a is formed on the tip end face of the inner side-wall-forming elongated projection 38 of the upper wall 31 and extends in the longitudinal direction of the inner side-wall-forming elongated projection 38 along the entire length thereof .
  • the projection 39a is press-fitted into the groove 38a .
  • Each of the reinforcement walls 35 is formed such that a reinforcement-wall-forming elongated projection 40 , which is integrally formed with the upper wall 31 in a downward raised condition , and a reinforcement-wall-forming elongated projection 41 , which is integrally formed with the lower wall 32 in an upward raised condition , are brazed together while butting against each other .
  • the flat tube 30 is manufactured by use of a flat-tube- forming metal sheet 45 as shown in FIG . 10 ( a) .
  • the flat- tube-forming metal sheet 45 is formed by performing rolling on an aluminum brazing sheet having a brazing material layer over opposite surfaces thereof .
  • the flat-tube-forming metal sheet 45 includes a flat upper-wall-forming portion 46 ( flat- wall-forming portion) ; a flat lower-wall-forming portion 47 ( flat-wall-forming portion) ; a connection portion 48 connecting the upper-wall-forming portion 46 and the lower- wall-forming portion 47 and adapted to form the right side wall 34 ; the inner side-wall-forming elongated projections 38 , 39 , which are integrally formed with the side ends of the upper-wall-forming and lower-wall-forming portions 46 , 47 opposite the connection portion 48 in an upward raised condition and which are adapted to form an inner portion of the left side wall 33 ; an outer side-wall-forming-elongated- projection forming portion 49 , which extends outward (rightward) with respect to the left-right direction from the side end ( right side end) of the upper-wall-forming portion 46 opposite the connection portion 48 ; and a plurality of reinforcement-wall-forming elongated projections 40 , 41 , which are integrally formed with the upper-wall-
  • the reinforcement-wall- forming elongated projections 40 of the upper-wall-forming portion 46 and the reinforcement-wall-forming elongated projections 41 of the lower-wall-forming portion 47 are located symmetrically with respect to the centerline of the connection portion in the width direction .
  • the projection 39a is formed on the tip end face of the inner side-wall- forming elongated projection 39 of the lower-wall-forming projection 47
  • the groove 38a is formed on the tip end face of the inner side-wall-forming elongated projection 38 of the upper-wall-forming portion 46.
  • the two inner side- wall-forming elongated projections 38 , 39 and all the reinforcement-wall-forming elongated projections 40 , 41 have the same height .
  • the inner side-wall-forming elongated projections 38 , 39 and the reinforcement-wall-forming elongated projections 40 , 41 are integrally formed, through rolling , on one side of the aluminum brazing sheet whose opposite sides are clad with a brazing material , whereby a brazing material layer (not shown ) is formed on the opposite side surfaces and tip end faces of the inner side-wall-forming elongated projections 38 , 39 , on those of the reinforcement-wall-forming elongated projections 40 , 41 , and on the vertically opposite surfaces of the upper-wall-forming and lower-wall-forming portions 46 , 47 , and the side-wall-forming-elongated-projection forming portion 49.
  • the flat-tube-forming metal sheet 45 is gradually folded at left and right side edges of the connection portion 48 by a roll forming process ( see FIG . 10 (b ) ) until a hairpin form is assumed .
  • the inner side-wall-forming elongated projections 38 , 39 are caused to butt against each other; the reinforcement-wall-forming elongated projections 40 , 41 are caused to butt against each other ; and the projection 39a is caused to be press-fitted into the groove 38a.
  • the outer side-wall-forming-elongated-projection forming portion 49 is folded along the outer surfaces of the inner side-wall-forming elongated projections 38 , 39 , and a tip end portion thereof is deformed so as to be engaged with the lower-wall-forming portion 47 , thereby yielding a folded member 50 ( see FIG . 10 ( c ) ) .
  • the folded member 50 is heated at a predetermined temperature so as to braze together tip end portions of the inner side-wall-forming elongated projections 38 , 39 ; to braze together tip end portions of the reinforcement-wall-forming elongated projections 40 , 41 ; and to braze the outer side-wall-forming-elongated-projection forming portion 49 to the inner side-wall-forming elongated projections 38 , 39 and to the lower-wall-forming portion 47.
  • the flat tubes 30 are manufactured in the course of manufacture of the heat exchanger 1 , 20.
  • a projection 56 extending along the entire length thereof and a groove 57 extending along the entire length thereof are alternately formed on the tip end faces of all the reinforcement-wall-forming elongated projections 40 of the upper wall 31.
  • a groove 58 into which the corresponding projection 56 of the reinforcement-wall-forming elongated projection 40 of the upper wall 31 is fitted, and a projection 59 to be fitted into the corresponding groove 57 of the reinforcement-wall-forming elongated projection 40 of the upper wall 31 are alternately formed on the tip end faces of all the reinforcement-wall-forming elongated projections 41 of the lower wall 32 , along the entire length thereof .
  • Other structural features are similar to those of the flat tube 30 shown in FIGS . 8 and 9.
  • the flat tube 55 is manufactured in a manner similar to that for the flat tube 30 shown in FIGS . 8 and 9.
  • the upper and lower walls 31 , 32 have projections 63 extending along the entire length thereof and formed integrally at portions thereof which abut the corresponding reinforcement-wall- forming elongated projections 62 , 61 ; grooves 64 are formed on the corresponding tip end faces of the projections 63 so as to allow corresponding tip end portions of the reinforcement-wall-forming elongated projections 61 , 62 to be fitted thereinto ; and the tip end portions of the reinforcement-wall-forming elongated projections 61 ,
  • the thickness of the projection 63 as measured in the left-right direction is slightly greater than that of the reinforcement-wall-forming elongated projections 61 , 62.
  • Other structural features of the flat tube 60 are similar to those of the flat tube 30 shown in FIGS . 8 and 9.
  • the width of each of the refrigerant channels 36 except for the refrigerant channel 36 at the right end, is not uniform along the height of the refrigerant channel 36.
  • the minimum channel width Wp of these refrigerant channels 36 means the width of the refrigerant channel 36 as measured at a certain height where the refrigerant channel 36 is the narrowest ; i . e .
  • each of the reinforcement-wall-forming elongated projections 61 , 62 serving as the reinforcement walls 35 is the thickness of a partition wall between the adjacent refrigerant channels 36.
  • the flat tube 60 is manufactured by use of a flat-tube- forming metal sheet 65 as shown in FIG . 14 ( a) .
  • the flat- tube-forming metal sheet 65 is formed by performing rolling on an aluminum brazing sheet having a brazing material layer over opposite surfaces thereof .
  • the flat-tube-forming metal sheet 65 includes a plurality of reinforcement-wall-forming elongated projections 61 , 62 , which are integrally formed with the upper-wall-forming and lower-wall-forming portions 46 , 47 in an upward raised condition and which are arranged at predetermined intervals in the left-right direction .
  • the reinforcement-wall-forming elongated projections 61 of the upper-wall-forming portion 46 and the reinforcement-wall- forming elongated projections 62 of the lower-wall-forming portion 47 are located asymmetrically with respect to the centerline of the connection portion 48 in the width direction .
  • the reinforcement-wall-forming elongated projections 61 , 62 have the same height , which is about two times the height of the inner side-wall-forming elongated projections 38 , 39.
  • the projections 63 which extend along the entire length of the upper-wall-forming and lower-wall- forming portions 46 , 47 , are integrally formed on the upper- wall-forming and lower-wall-forming portions 46 , 47 at positions which are symmetrical , with respect to the centerline of the connection portion 48 in the width direction , with the positions of the reinforcement-wall- forming elongated projections 62 , 61 of the lower-wall- forming and upper-wall-forming portions 47 , 46.
  • the grooves 64 are formed on the corresponding tip end faces of the projections 63 so as to allow corresponding tip end portions of the reinforcement-wall-forming elongated projections 62 , 61 to be fitted thereinto .
  • Other structural features of the flat-tube-forming metal sheet 65 are similar to those of the flat-tube-forming metal sheet 45 shown in FIG . 10.
  • the flat-tube-forming metal sheet 65 is gradually folded at left and right side edges of the connection portion 48 by a roll forming process ( see FIG . 14 ( b ) ) until a hairpin form is assumed .
  • the inner side-wall-forming elongated projections 38 , 39 are caused to butt against each other , and the projection 39a is caused to be press-fitted into the groove 38a .
  • tip end portions of the reinforcement- wall-forming elongated projections 61 of the upper-wall- forming portion 46 are caused to be fitted into the corresponding grooves 64 of the projections 63 of the lower- wall-forming portion 47
  • tip end portions of the reinforcement-wall-forming elongated projections 62 of the lower-wall-forming portion 47 are caused to be fitted into the corresponding grooves 64 of the projections 63 of the upper-wall-forming portion 46.
  • the outer side-wall-forming-elongated-projection forming portion 49 is folded along the outer surfaces of the inner side-wall-forming elongated projections 38 , 39 , and a tip end portion thereof is deformed so as to be engaged with the lower-wall-forming portion 47 , thereby yielding a folded member 66 ( see FIG . 14 ( c ) ) .
  • the folded member 66 is heated at a predetermined temperature so as to braze together tip end portions of the inner side-wall-forming elongated projections 38 , 39 ; to braze tip end portions of the reinforcement-wall- forming elongated projections 61 , 62 to the corresponding projections 63 ; and to braze the outer side-wall-forming- elongated-projection forming portion 49 to the inner side- wall-forming elongated projections 38 , 39 and to the lower- wall-forming portion 47.
  • the flat tubes 60 are manufactured in the course of manufacture of the heat exchanger 1 , 20.
  • the reinforcement walls 35 of a flat tube 70 shown in FIGS . 15 and 16 are formed such that reinforcement-wall- forming elongated projections 71 , 72 formed integrally with the upper wall 31 and in a downward raised condition are caused to butt against and brazed to reinforcement-wall- forming elongated projections 73 , 74 formed integrally with the lower wall 32 and in an upward raised condition .
  • the high and low reinforcement-wall-forming elongated projections 71 and 72 which differ in projection height , are alternately provided in the left-right direction on the upper wall 31
  • the high and low reinforcement-wall-forming elongated projections 73 and 74 which differ in projection height , are alternately provided in the left-right direction on the lower wall 32.
  • the reinforcement-wall-forming elongated projections 71 of large projection height on the upper wall 31 are brazed to the reinforcement-wall-forming elongated projections 74 of small projection height on the lower wall 32 ; and the reinforcement-wall-forming elongated projections 72 of small projection height on the upper wall 31 are brazed to the reinforcement-wall-forming elongated projections 73 of large projection height on the lower wall 32.
  • first reinforcement-wall-forming elongated projections the reinforcement-wall-forming elongated projections 71 , 73 of large projection height provided on the upper and lower walls 31 and 32 , respectively.
  • second reinforcement-wall-forming elongated projections the reinforcement-wall-forming elongated projections 72 , 74 of small projection height provided on the upper and lower walls 31 and 32 , respectively.
  • Grooves 75 , 76 which extend along the longitudinal direction , are formed on the corresponding tip end faces of the second reinforcement-wall- forming elongated projections 72 , 74 of the upper and lower walls 31 , 32 over the entire length so as to receive the corresponding tip end portions of the first reinforcement- wall-forming elongated projections 73 , 71 of the lower and upper walls 32 , 31.
  • the reinforcement-wall-forming elongated projections 71 74 , and the reinforcement-wall-forming elongated projections 72 , 73 are brazed together in a state in which the corresponding tip end portions of the first reinforcement-wall-forming elongated projections 71 , 73 of the upper and lower walls 31 and 32 are fitted into the grooves 76 , 75.
  • Other structural features of the flat tube 70 are similar to those of the flat tube 30 shown in FIGS . 8 and 9.
  • the width of each of the refrigerant channels 36 except for the refrigerant channel 36 at the right end, is not uniform along the height of the refrigerant channel 36.
  • the minimum channel width Wp of these refrigerant channels 36 means the width of the refrigerant channel 36 as measured at a certain height where the refrigerant channel 36 is the narrowest ; i . e . , the distance between the first reinforcement -wall-forming elongated projection 71 or 73 and the second reinforcement- wall-forming elongated projection 72 or 74 adjacent thereto .
  • the thickness of each of the first reinforcement-wall-forming elongated projections 71 , 73 is the thickness of a partition wall between the adjacent refrigerant channels 36.
  • the grooves 75 , 76 extent over the entire height of the second reinforcement-wall-forming elongated projections 72 and 74 ; however , the present invention is not limited thereto , and the depth of the grooves 75 , 76 may be smaller than the height of the second reinforcement-wall-forming elongated projections 72 and 74.
  • the flat tube 70 is manufactured by use of a flat-tube- forming metal sheet 80 as shown in FIG . 17 ( a) .
  • the flat- tube-forming metal sheet 80 is formed by performing rolling on an aluminum brazing sheet having a brazing material layer over opposite surfaces thereof .
  • the flat-tube-forming metal sheet 80 includes a plurality of reinforcement-wall-forming elongated projections 71 , 72 , 73 , 74 , which are integrally formed with the upper-wall-forming and lower-wall-forming portions 46, 47 in an upward raised condition and which are arranged at predetermined intervals in the left-right direction.
  • the first reinforceinent-wall-forming elongated proj ections 71 of the upper-wall-forming portion 46 and the second reinforcement-wall-forming elongated proj ections 74 of the lower-wall-forming portion 47 are located symmetrically with respect to the centerline of the connection portion 48 in the width direction .
  • the second reinforcement- wall-forming elongated proj ections 72 of the upper-wall- forming portion 46 and the first reinforcement-wall-forming elongated proj ections 73 of the lower-wall-forming portion 47 are located symmetrically with respect to the centerline of the connection portion 48 in the width direction.
  • the grooves 75, 76 are formed on the corresponding tip end faces of the second reinforcement-wall-forming elongated proj ections 72 , 74 of the upper-wall-forming and lower-wall- forming portions 46, 47 so as to allow corresponding tip end portions of the first reinforcement-wall-forming elongated proj ections 73 , 71 of the lower-wall-forming and upper-wall- forming portions 47 , 46 to be fitted thereinto .
  • Other structural features of the flat-tube-forming metal sheet 80 are similar to those of the flat-tube-forming metal sheet 45 shown in FIG . 10.
  • the flat-tube-forming metal sheet 80 is gradually folded at left and right side edges of the connection portion 48 by a roll forming process (see FIG . 17 (b) ) until a hairpin form is assumed.
  • the inner side-wall-forming elongated projections 38 , 39 are caused to butt against each other .
  • tip end portions of the first reinforcement-wall- forming elongated projections 71 , 73 are caused to be fitted into the corresponding grooves 76 , 75 of the second reinforcement-wall-forming elongated projections 74 , 72.
  • the projection 39a is caused to be press -fitted into the groove 38a.
  • the outer side-wall-forming-elongated-projection forming portion 49 is folded along the outer surfaces of the inner side-wall-forming elongated projections 38 , 39 , and a tip end portion thereof is deformed so as to be engaged with the lower-wall-forming portion 47 , thereby yielding a folded member 85 ( see FIG . 17 ( c ) ) .
  • the folded member 85 is heated at a predetermined temperature so as to braze together tip end portions of the inner side-wall-forming elongated projections 38 , 39 ; to braze tip end portions of the first reinforcement- wall-forming elongated projections 71 , 73 to tip end portions of the second reinforcement-wall-forming elongated projections 74 , 72 ; and to braze the outer side-wall-forming- elongated-projection forming portion 49 to the inner side- wall-forming elongated projections 38 , 39 and to the lower- wall-forming portion 47.
  • the flat tubes 70 are manufactured in the course of manufacture of the heat exchanger 1 , 20.
  • the flat tubes 30 , 55 , 60 , 70 of modified embodiments described above also satisfy the above-mentioned Relations 1 to 7 .
  • the heat exchanger according to the present invention is preferably used as a gas cooler of a supercritical refrigeration cycle which uses a supercritical refrigerant such as CO 2 and in which the pressure of the refrigerant on a high-pressure side becomes equal to or higher than the critical pressure of the refrigerant .

Abstract

L'invention concerne un échangeur de chaleur (1) qui comprend deux collecteurs (2, 3) disposés à l'opposé l'un de l'autre, et une pluralité de tubes plats (4) disposés entre les deux collecteurs (2, 3) à des intervalles prédéterminés dans le sens longitudinal des deux collecteurs (2, 3), chacun possédant des parties d'extrémité opposées reliées aux collecteurs respectifs (2, 3) et présentant une forme de section transversale identique. Tous les tubes plats (4) sont divisés en deux passages (P1, P2), chacun étant constitué d'une pluralité de tubes plats (4) disposés en continu dans le sens vertical. En divisant le nombre de tubes plats (4) qui constituent chacun des passages (P1, P2) par le nombre représentant la totalité des tubes plats (4), on obtient un quotient défini en tant que 'rapport de tubes' ; chacun des passages (P1, P2) présentant un rapport de tubes compris entre 0,45 et 0,55 ; de préférence entre 0,48 et 0,52. Ledit échangeur de chaleur (1) peut être utilisé en tant que refroidisseur de gaz pour un cycle de réfrigération supercritique et offrir une performance de rayonnement thermique améliorée tout en présentant une taille et un poids réduits.
PCT/JP2005/023695 2004-12-24 2005-12-19 Echangeur de chaleur WO2006068262A1 (fr)

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Application Number Priority Date Filing Date Title
DE112005003260T DE112005003260T5 (de) 2004-12-24 2005-12-19 Wärmetauscher

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2004-372590 2004-12-24
JP2004372590 2004-12-24
US64006304P 2004-12-30 2004-12-30
US60/640,063 2004-12-30

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WO (1) WO2006068262A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2928448A1 (fr) * 2008-03-04 2009-09-11 Valeo Systemes Thermiques Refroidisseur de gaz ameliore
CN104620069A (zh) * 2012-09-04 2015-05-13 夏普株式会社 并流式热交换器和安装有该并流式热交换器的空气调节机
EP3492853A1 (fr) * 2017-11-29 2019-06-05 Lennox Industries Inc. Échangeur de chaleur à microcanaux
EP4174431A1 (fr) * 2021-11-02 2023-05-03 Carrier Corporation Tube d'échange de chaleur fabriqué pour échangeur de chaleur à microcanaux

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Publication number Priority date Publication date Assignee Title
JP2000356488A (ja) * 1999-06-11 2000-12-26 Showa Alum Corp 熱交換器用チューブ
JP2001027484A (ja) * 1999-07-15 2001-01-30 Zexel Valeo Climate Control Corp サーペンタイン型熱交換器
WO2002095302A1 (fr) * 2001-05-23 2002-11-28 Matsushita Electric Industrial Co., Ltd. Dispositif a cycle de refrigeration
JP2003053460A (ja) * 2001-06-08 2003-02-26 Showa Denko Kk 偏平管製造用金属板、偏平管および偏平管の製造方法
JP2003166790A (ja) * 2001-11-29 2003-06-13 Mitsubishi Heavy Ind Ltd 熱交換器
JP2004271116A (ja) * 2003-03-11 2004-09-30 Japan Climate Systems Corp 熱交換器のフィン構造

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000356488A (ja) * 1999-06-11 2000-12-26 Showa Alum Corp 熱交換器用チューブ
JP2001027484A (ja) * 1999-07-15 2001-01-30 Zexel Valeo Climate Control Corp サーペンタイン型熱交換器
WO2002095302A1 (fr) * 2001-05-23 2002-11-28 Matsushita Electric Industrial Co., Ltd. Dispositif a cycle de refrigeration
JP2003053460A (ja) * 2001-06-08 2003-02-26 Showa Denko Kk 偏平管製造用金属板、偏平管および偏平管の製造方法
JP2003166790A (ja) * 2001-11-29 2003-06-13 Mitsubishi Heavy Ind Ltd 熱交換器
JP2004271116A (ja) * 2003-03-11 2004-09-30 Japan Climate Systems Corp 熱交換器のフィン構造

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2928448A1 (fr) * 2008-03-04 2009-09-11 Valeo Systemes Thermiques Refroidisseur de gaz ameliore
CN104620069A (zh) * 2012-09-04 2015-05-13 夏普株式会社 并流式热交换器和安装有该并流式热交换器的空气调节机
CN104620069B (zh) * 2012-09-04 2016-08-31 夏普株式会社 并流式热交换器和安装有该并流式热交换器的空气调节机
EP3492853A1 (fr) * 2017-11-29 2019-06-05 Lennox Industries Inc. Échangeur de chaleur à microcanaux
EP4174431A1 (fr) * 2021-11-02 2023-05-03 Carrier Corporation Tube d'échange de chaleur fabriqué pour échangeur de chaleur à microcanaux

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